Fluid pump



April 4, 1944.

G. T. DQWNEQYI FLUID PUMP Filed April 2, 1941 6 Sheets-Sheet l April 4, 1944- G. 'r. DOWNEY 2,346,014

FLUID PUMP Filed April 2. 1941 GSheets-Sheet 2 swam tom April 4, 1944. a. 'r. DOWNEY FLUID PUMP Filed April 2, 1941 6 Sheets-Sheet 3 M W M J @Jffiawrzey P 1944- I G. T. DOWNEY v 2,346,014

FLUID PUMP Filed April 2, 1941 6 Sheets-Sheet 4 OUT April 4, 1944. 5. T. DOWNEY FLUID PUMP Filed April 2, 1941 '6 Sheets-Sheet 5 April 4, 1944. DQWNEY 2,346,014

FLUID PUMP Filed April 2, 1941 6 Sheets-Sheet 6 6 M9 we 5 zar Z0 200 A Z07 6. Z: Pei x716 3 wow/1a I Q/ZZ/ i O/ZZZ atented Apr. 4, 1944 FLUID PUMP George '1. Downey, Corry, Pas, assignor to Aero Supply Mfg. Co. Inc., Corry, Pm

Application April 2, 1941, Serial No. 386,542

11 Claims.

This invention relates to fluid pumps.

An object of this invention is to provide a pump including a rotary pumping element wherein the element is formed of correlated pumping members movable one relative to the other during the rotation of both members, so as to provide for alternate intake and exhaust of the fluid.

Another object of this invention is to provide in a pump of this kind an improved arrangement of the intake and exhaust passages so as to provide a cyclic action during the rotation of the rotary parts.

A further object of this invention is to provide a pump or this kind in which the rotor elements are moved relative to each other by means of intermeshing eccentrically arranged gears providing a smooth positive rotary action, which will eliminate vibration.

A further object of this invention is to provide in a rotary pump a cast pump body or housing and an improved port forming liner for the rotor, the liner being provided with circumferentially arranged elongated ports with certain of the ports communicating with each other and also with an outlet or inlet port.

A further object of this invention is to provide in a pump of this kind an insertible liner having a plurality of superposed circumferentially arranged inwardly facing elongated fluid passages disposed in circumferentially arranged pairs with one passage of each pair in communication, either directly or indirectly, with an inlet port and the other passage of each pair in communication, either directly or indirectly, with an outlet port.

A further object of this kind is to provide in a pump, rotary pumping members and gear means for efiecting a relatively quick movement of said members relative to each other during one suction and exhaust cycle thereof coactive with the rotation of said members as a unit and a retarded movement of said members in another cycle thereof.

To the foregoing objects and to others which may hereinafter appear, the invention consists of the novel construction, combination and arrangement of parts as will be more specifically referred to and illustrated in the accompanying drawings, wherein are shown embodiments of the invention, but it is to be understood that changes, variations and modifications may be resorted to which fall within the scope of the invention as claimed.

In the drawings:

Figure l is a vertical section taken through a 4-4 of Figure 1,

fluid pump constructed according to an embodl ment of this invention,

Figure 2 is a sectional view taken on the line 2--2 of Figure 1,

Figure 3 is a sectional view taken on the line 3-3 of Figure 1,

Figure 4 is a sectional view taken on the line Figure 5 is a sectional view taken 5-5 of Figure 1,

Figure 6 is a fragmentary sectional view taken on the line 6-t of Figure 1,

Figure 7 is a plan view of the liner in extended form,

Figure 8 is a plan view of the rotary piston in extended form. I

Figure 9 is a top plan of one pair of the pumping blades,

Figure 10 is an end elevation of the structure shown in Figure 9,

Figure 11 is an outer end elevation of one of the other pair of pumping blades showing a portion of the rotor in section,

Figure 12 is a sectional view taken on the line 92-42 of Figure 1,

Figure 13 is a vertical section partly in detail of a modified form of this invention,

Figure 14 is a sectional view taken on the M-lt of Figure 13,

Figure 15 is a fragmentary sectional view taken line a on the line l5-l5 oi Figure 13,

Figure 16 is a plan view of the liner used with the form shown in Figure 13, the liner'being shown in extended form, and

Figure 1'? is a plan view of the rotor in extended form which is used with the structure shown in Figure 13.

Referring to the drawings and first to Figures 1 to 12 inclusive, the numeral 20 designates generally a housing which includes a cylindrical body 2i and a gear housing or chamber 22, which extends from one end, and in the present instance the lower or inner end of the cylinder 2|. The cylinder 2! is provided with a boss 23 having an intake passage it with which an intake pipe 25 is adapted to be threadably connected. The cylinder 2! is also provided with a second boss 26 having an outlet or exhaust passage N, with which an outlet or exhaust pipe 20 is adapted to be threadably connected. The cylinder 2!, as shown in Figure 3, is formed with a relatively long intake opening 29 communicating with the intake port it and the cylinder 21 is also provided with a relatively long outlet or exhaust passage 30 communicating with th exhaust port 21.

on the line A cap or head 3| is mounted on the outer or upper end of the cylinder 2| and is provided with an annular flange or rib 32 engaging within the cylinder 2|. A sealing gasket 33 is adapted to be interposed between the cap or head 3| and the outer end portion of the cylinder 2|. Fastening devices 34 are adapted to removably secure the head 3| on the cylinder 2|. The fastening devices 32 are preferably locked against rotation when they are tightened by means of a locking wire 35, which is extended through suitable openingsprovlded in the heads of the fastening members 34.

A liner, generally designated as 36, is fixedly disposed within the cylinder 2| and this liner is of cylindrical construction, but preferably pressed or otherwisefirmly held within the cylinder 2|. The liner 38 is constructed of metal which may be different in character from the metal or material forming the cylinder 2| and the liner 38 provides a means whereby combined rotation of the pumping structure disposed therein may be alternately placed in communication with the inlet and outlet ports of the cylinder 2|. In Figure 7 the liner 36 is shown in extended form in order to more clearly show the various inlet and outlet ports formed therein. As shown in Figure 7, the liner 38 is provided with a plurality of pairs of inlet and outlet openings or passages spaced from each other longitudinally of the liner, the passages being of elongated configuration and extended entirely through the liner 36.

The liner 38 is provided adjacent the upper portion thereof with an elongated outlet passage 31 and an elongated inlet passage 38. The outlet passage 31 is substantially longer than the inlet passage 38, and a dividing wall or partition 38 divides the two adjacent ends of the passages 31 and 38 from each other, whereas a second dividing wall 43 divides the opposite ends of the passages 31 and 38 so as to prevent communication between the two inlet and outlet passages.

A second pair of fluid passages is disposed bellow the upper passages 31 and 38 and comprise a relatively long inlet passage 4| and a substantially shorter outlet passage 42. The passages 4| and 42 at one end thereof are separated by a dividing wall 43 and at the other end thereof are separated by a dividing wall 44. The upper outlet passage 31 is adapted to communicate with the intermediate outlet passage 42 by means of a communicating passage 45. The upper inlet passage 38 is adapted to communicate with the intermediate inlet passage 4| by means of a com.- municating passage 48. The communicating passages 45 and 48 are formed as slots in the outer face of the liner 38. A third pair of passages is disposed below the intermediate passages 4| and 42 and comprise a relatively long outlet passage 41 and a substantially shorter inlet passage 48.

The passages 41 and 48 are separated at one end thereof by a partition or dividing wall 49 and at the other end thereof are separated by a dividing wall 58. The inlet passage 48 is in communication with the inlet passage 4| through a communicating slo or passage formed in the outer face of the liner 38 and the outlet passage 41 is in communication with the outlet passage 42 by means of a communicating passage 52 formed in the outer face of the cylinder 38 between the wall 43 and the wall 49. The communicating passage 5| is positioned between the wall 44 and the wall 58.

A lower pair of fluid passages 53 and 54 is disposed below the passages 41 and 48, the passage 53 being a substantially long inlet passage and the passage 54 being a substantially shorter but elongated outlet passage. The inlet passage 53 is in communication with the inlet passage 48 by means of a communicating passage 55, and the passage 54 is in communication with the passage- 41 by a communicating passage 56. The communicating passages 55 and 58 are formed as slots in the outer face of the liner 36. The inlet passage 4| is disposed in registry with the inlet port 26 and the outlet passage 42 is in registry with the outlet port 30. The inlet and outlet passages 4| and 42 are of substantially greater length than the inlet and outlet ports 23 and 38 respectively, as shown in Figure 7.

As shown in Figure 7 the arrangement of the long inlet and outlet passages in the liner 38 is such that a long outlet passage will extend partly over the entire length of a lower or succeeding outlet passage and will extend partly or substantially for one-half the length of a lower inlet passage. In like manner the long lower inlet passage such as passage 4| extends substantially over the entire length of the upper inlet passage 38 and extends substantially one-half of the length of the next succeeding lower inlet passage 48. By staggering the positions of the pairs of inlet and outlet passages, it is possible to provide a rotor pump structure, to be hereinafter described, which will include a rotary piston and also include rotary pumping blades for alternately exhausing and drawing in the fluids through the inlet and outlet passages.

The liner 38 is adapted at its inner or lower end to seat on the lower or inner end 51 of the cylinder 2|, and the upper or outer end of'the liner 38 is provided with an annular groove 58 within which the rib 32 is adapted to engage. Preferably the liner 38 at its upper or outer end terminates inwardly from the outer end of the cylinder 2| so as to thereby form an annular lubricant duct or channel 58.

A rotary piston, generally designated as". is rotatably disposed within the interior of the liner 38 and includes a cylindrical side wall 8|, 9. fiat inner head or wall 82 and a disc-shaped outer wall or head 83. The cylindrical side wall 6| is formed with an inwardly facing groove or rabbet 84 within which the head 83 is adapted to seat. The inner head 82 is provided with a downwardly extending socket member 85, which is formed with a cylindrical outer surface and with a nut socket 86, the purpose for which will be hereinafter described.

The cylinder 88 has fixedly mounted therein a pair of diametrically opposed blades, generally designated as 81 and 88. The blades 61 and 83 are of like construction and extend from the inner to the outer end of the cylindrical side wall 8| of the piston 88. In transverse section the blades 61 and 88 are of sector shape and include a pair of inwardly convergent side walls 89 and 18, which are fiat and the blades 81 and 88 also include fiat upper and lower walls 1| and 12 respectively. The blades 81 and 68 are fixedly secured to the bottom wall or head 82 of the piston by means of a holding pin 13 which is fixedly mounted in a boss or bushing 1.4, which extends upwardly from and formed integral with the bottom wall 12. The pin 13 projects downwardly below the bottom wall 12 and engages in an opening 15 formed in the inner head 82. The blade 81 is also formed with an inner transversely arcuate wall 18. The outer ends of the side walls 89 and 10 of the blade 81 are formed with opposed flanges 11 and 10 respectively, which are adapted to snugly engage within the inner surface of the cylindrical side wall I.

The blade 61 is formed adjacent the upper portiorrof the side wall 69 with a passage 19 and the side wall I0 is formed adjacent the lower end thereof with a passage 00. The passage I0 is disposed in a position for registry with the upper pair of passages 31 and 30, and the lower passage 00 of the blade 61 is disposed in a position for registry with the lower pair of elongated liner passages 53 and 54. The blade 68 is similar in every detail to the blade 01, with the exception that the blade 60 is formed with passages similar to the passages I9 and 80, which are adapted to register with the elongated passages 4i and 42 and the passages 41 and 48. The cylindrical side wall SI of the piston 60 is provided with an upper opening 8| adapted to register with the passage I9 of the blade B'Iand is also provided with a lower opening 82 disposed in registry with the passage 80. The side wall 0| is also provided with a pair of intermediate openings 83 and 24 adapted to register with side openings provided in the blade 68 similar to the passages I9 and 00 of the blade 61.

A pair of rotary pumping blades generally designated as 85 and 80 are disposed within the piston 60 between the blades 01 and 68. The rotary blades 85 and 00 are of like construction and as shown in Figure 9, are each of sectorshape in transverse section and include inwardly convergent flat side walls 81 and 08 and flat top and bottom walls 89 and 00. A pair of opposed flanges 0| and 92 are carried by the side walls 01 and 80. Each rotary blade is also provided with a transversely arcuate inner wall 93, which is adapted to engage against a cylindrical shaft or sleeve-94. The two rotary blades and 80 are fixedly secured to the sleeve or hollow shaft 94 by means of a pair of horizontally disposed bolts or fastening members 95, which extend through enlargements 96 formed between the side walls 01 and 80 and which extend outwardly from the inner wall 93, as shown in Figure 4.

The-hollow shaft 94 has formed. integral therewith a second hollow shaft 91, which is of smaller diameter than the shaft 04 and extends therefrom into the gear chamber 22. The hollow shaft 91 extends through the socket member 65, as shown in Figure 1, and is of substantially smaller diameter than the interior of the nut socket 00. A drive shaft 98 is disposed concentrically of the hollow shaft members 94 and 91 and is provided with a pair of enlargements 00 and I00 through which the bolts or fastening members 05 engage, so that the sleeve shaft 04 will rotate as a unit with the drive shaft 08. The enlargements 99 and I00 are annular in, transverse section and are spaced apart along the shaft 08 being positioned entirely within the sleeve shaft 04. as shown in Figure 1. longer than the sleeve shaft 01 and is provided with an extension I0| which, as shown in Figure 12, is square in transverse section and a splined coupling member I02 is mounted on the square shaft member IOI being secured thereon by means of a holding nut I03 which is threadably mounted on a threaded stud I04 carried by the square shaft IN.

The splined coupling member I02 is positioned exteriorly of the gear chamber 22 and provides a means whereby the drive shaft 98 may be detachably coupled with a suitable driving means. The driving means may be in the form of a small motor or may be in the form of a driving connection with an internal combustion engine, such as an aeroplane engine or the like.

The head 03 is provided with an axial stud I05 which rotatably engages in a socket or recess I00 formed in the outer or upper end of the enlargement I00, as shown in Figure l. The head 63 is also provided with a second stud I01, which is substantially smaller in diameter than the stud I05 and the stud I0'I is mounted in an inner antifriction race member I08.

The cap or head member 3| is provided with an outwardly or upwardly offset bushing I within which the outer race IIO of an anti-friction bearing is snugly positioned. Anti-friction balls III engage between the two race members I00 and H0. The anti-friction bearing structure including the race members I08, I I0 and the balls III provides a means for rotatably supporting the outer or upper end of the rotary piston 60 within the liner 38. i

The gear chamber 22 extends inwardly or downwardly from the cylinder 2| and is of smaller diameter or size than the cylinder 2|, being formed with a side wall structure II2, which ex-- tends from the inner wall 51 of the cylinder 2I and also includes an inner wall or head H3. The head II3 inthe present instance is formed integral with the side wall H2 and a flange II4 extends outwardly from the head or inner wall 3. The upper or inner end of the gear chamber 22 has positioned therein a plate or head H5,

- which may be pressed or otherwise tightly disposed in the interior of the gear chamber 22. The plate or head H5 is provided with an opening IIO therethrough and within which the hollow shaft 05 rotatably engages.

A flanged gasket III is preferably interposed between the sleeve 00 and the wall of the opening N6, the flange II8 of the gasket III engaging on the upper surface of the head H5 and between the' head I I5 and the inner wall or head 62 of the piston 60. In this manner the flange II8 forms a lubricant passage IIQ between the head 62 and the head or plate H5. A cylindrical bushing or sleeve I20 is snugly mounted in an opening I2I formed in the head III and the lower end of the sleeve shaft 01 is adapted to rotatably The drive shaft 90 is substantially engage within the sleeve or hearing member I20. The bearing member I20 at its inner end is provided with a flange I22, which engages against the inner side of the head H3 and prevents the outward movement of the bearing sleeve I20.

A driving gear I23 is fixedly mounted on the sleeve shaft 01 above the bushing 20, the sleeve shaft 01 being provided with flattened surfaces, which are engaged by the gear I 23 so as to hold the gear I23 against rotation relative to the sleeve shaft 91. The shaft 01 engages through the gear I23 at one side of the axial center of the gear I23, as shown in Figures 1 and 6. The gear I23 meshes with a gear I24, which is fixedly secured as by a key I25 to a jack shaft I20. The shaft I20 is provided with an eccentrically disposed an nular gear shaft I21 on which the gear I24 is fixedly mounted. The eccentric shaft member I2'I' is also positioned eccentrically of the axial ed on the sleeve shaft 91 and is provided with a pair of nut members H2 and I33. The nut member I33 engages within the nut socket 66 so that the sleeve I 3! will be held against rotation rela tive to the sleeve member-$5 and the piston 69. A gear member N35 is mounted on the nut member I32, being disposed with the axial center oilset with respect to the axial center of the sleeve 335. The gear lid is in constant mesh with the gear I28 so that rotation of the gear ifid will effect the rotation of the piston 56.

By providing the intermeshing pairs of eccen trically disposed driving gears for the piston Gil, the piston 60 is given a plurality of different speeds during each complete rotation thereof so that the eliect of this variation in the speed of the rotation of the piston or rotor 5b is to con= stitute the blades El and 5t oscillatory blades which oscillate back and forth with respect to the rotary blades 85 and 86 carried by the rotary sleeve shaft 9%.

The lower end of the jack shaft 628 is mounted in an inner anti-friction race member i3? and an outer anti-friction race member I36 is snugly mounted in a recess it? formed in the head Hi3. Anti-friction balls I38 are interposed between the two race members HE and 435. The opposite or inner end of the jack shaft lie is mounted in an inner race member I39, and an outer race member MS is mounted in a recess or socket it, which is formed in the plate or inner head tilt. Antl irictlon balls 052 are interposed between the race members $39 and Md. The two gears lid and I35 are held in spaced apart relation by means of a washer M3, which engages about the sleeve shaft bl. By providing the two nut members 532 and I33 on the sleeve shaft 5! a flange or rib IN is formed on the sleeve 83d against which the inner side of the gear its is adapted to abut.

The gears hereinbefore described are rotatably mounted in a combined gear and lubricant chamher IN. The chamber 22 has leading oil there from an outlet passage l i and a needle valve member id? is adapted to engage adjacent the outer end of the outlet passage Mid so as to regulate the amount of lubricant flowing out of the passage MB. The needle valve member i ll is threaded into a threaded bushing l li, which gages in the wall of the chamber 22, and a loci;

nut M8 is threaded onto the needle valve member l l'i so as to tightly hold the valve member i 'll in adjusted position.

The outlet passage Mil communicates with an enlarged lubricant chamber lbd and a downwardly extending passage 35! communicates at its upper end with the passage or chamber iiid. An inwardly extending passage M2 extends from the passage 55! and communicates with an opening I53 formed in the bushing i253, so that the lower portion of the sleeve shaft M will receive adequate lubricant. An upwardly extending lubricant passage 855 extends from the chamber lbs and communicates with an outwardly or laterally extending passage 555. An upwardly extending passage Mil is formed in an offset housing member 6% and extends upwardly to and opens into a slot 859, which may be formed in the gasket 33 so that the lubricant from the passage tb'l will flow through the slot its into the lubri cant passage 59.

The liner is provided with a downwardly extending lubricant passage Hill which at its upper end communicates with the passage 53 and a pair of inwardly extending branches or passages 968 asaaoia and I62 extend inwardly through the liner 36 and communicate with the inner annular grooves I63 and lid respectively, which are formed in the liner 36 between the upper pairs of inlet and outlet ports. The liner 36 may also be provided with an inwardly extending opening or lubricant passage l 65 communicating with the upper portion of the vertical channel or passage I68, so that the upper portion of the rotor will receive proper lubricant.

The upper or outer head $3 of the rotor 60 is spaced from the outer head 3| of the housing 20, thereby providing an outer lubricant chamber IE6, which communicates .with the lateral passage l and also communicates with the antifriction bearing comprising the race members I 08 and Ill] and the balls Hi. Preferably the bushing or boss ms is formed with a lubricant chamher it? outwardly of the anti-friction bearing and the two studs Hi5 and E01 are formed with a common axial lubricant passage I88.

The lubricant from the chamber I6! is adapted to flow downwardly or inwardly through the passage 85% and engage in a lubricant chamber "59 formed in the shaft enlargement I00 inwardly from the inner stud shaft I05. The enlargement Hid is provided with a plurality of radially arranged openings l'lli leading from the lubricant chamber I69, which register with lubricant openings ill formed in the sleeve shaft 9 5. The inner walls 533 of the rotaryblades 85 and 86 are formed with an inner lubricant passage I12, which communicates with the horizontal passage ill. The upper end of the passage H2 communicates with a groove H3 formed in the upper wall 89, and a pair of outwardly divergent grooves 574 communicate with the groove H3 and extend parallel with the side walls of the rotary blades 85 and t6.

The outer ends of the blades 85 and 86 are formed with outer lubricating grooves I communicating with the upper grooves i'l i so that the outer flanges 9i and 92 will receive proper lubricant. The outer vertical lubricant grooves or passages I75 connect with inwardly convergent grooves l'lli formed in the bottom walls of the rotary members, and the lower grooves I15 communicate with the lower ends of the vertical grooves or channels H2 by a connecting groove similar to the groove H3.

The liner 36 is also formed with a vertical lubricant duct or channel ill, which extends from substantially the longitudinal center of the liner 35 to the lower end thereof. The channel lll communicates at its upper end with an inwardly extending opening ilti, which also communicates with the annular groove it' l. A second inwardly extending opening H9 communicates at one end with the vertical passage Ill and at its other or inner end communicates with an annular groove I86 formed in the liner 36 below the groove ltd and between the passages ll, t8 and the passages 53 and. 5d.

The passage i ll at its lower end communicates through a slot i8i with the lower lubricant chamber H9. The lubricant in the chamber H5 is adapted to return to the reservoir Hi5 through the anti-friction hearing including the race members i3 9 and Hill and the balls M2. The cap or head Si is provided with an upstanding boss 962 having a threaded recess Hi3, so that a supporting means may be threaded into the boss 532 for supporting the housing 20 in the desired position.

In Figures 13 to 17 inclusive, there is disclosed another form or fluid pump assembly, which asaaoic includes a pump housing and rotary piston'with pumping blades therein similar in substantially every detail to the rotary piston, shown in Figures 1 to 13 inclusive. In this term there is provided a pump housing, generally designated as I94, which includes a cylinder I85 and a gear housing I96, which extends downwardly from the cylinder I95 The cylinder I99 has mounted therein a cylindrical liner I81, which is substantially similar in every detail to the liner 96, being provided with pairs of superposed fluid openings or passages which extend therethrough. The housing I9! is provided with a pair of bosses I99 and I99 having intake and outlet ports I99 and I9! respectively, which communicate with arouate intake and outlet ports 592 and I93 extending partly about the cylinder I96.

The liner I91 is provided with an upper elongated outlet port I94 and an elongated inlet port I99, the latter port being substantially shorter in length than the outlet port I94. also provided with a second pair oi ports below the upper ports I99'and I99, the second pair of ports includes an elongated inlet port I99 and an elongated outlet port I91, the latter port being substantially shorter in length than the inlet port I99. The outlet port I91 is in registry with the outlet port I92, but as shown in Figure 16, the elongated liner port I91 is substantially longer than the outlet port I92. A third pair of fluid ports is disposed below the ports I96 and I91, the third pair of ports including elongated o tlet port I99 and an elongated inlet port I99. inlet port I99 is substantially shorter in length'than the outlet port I99. w -A lower pair of ports is provided'in the liner I91 and includes a lower elongated inlet port 299 and a lower outlet port 2", thedatter'being substantially shorter in length than the inl'et port 200.

The outlet port :94 n in communication with the outlet port I91 by a communicating passage 292, which is formed in the outer side of the I99 is substantially longer than the port I92; The inlet port I96 is in communication with the relatively short inlet port I 99 by means or a com- The liner Illis nately yliner I91 and the upper inlet port-I99 is in communicating passage 299 formed in the outer, side formed in the outer side of the liner i91.

A rotor, generally designated as 299, is rotatably disposed within the liner I91 and includes 5 a cylindrical side wall 299, a bottom wall 2I9,

which is fixed to or formed integral with the ey lindrical side wall 299 and also includes a top wall or head 26 i, which seats in a rabbet or annularrecess 2I2 formed in the upper or outer end portion of the cylindrical side wall 299. The

inner wall or head 2I9 has formed integral therewith or fixed thereto a sleeve or hollow shaft 2I9, which is iormed with an inner nut socket 254.

29! by means oi a communicating passage 291' A pair of diametrically opposed pumping blades 2|! and H9 are fixedly mounted within the cylindrical side wall 299, and each blade H6 is of sector configuration in transverse section and is secured to the rotor 299 by means or a holding pin 2", which is mounted in a boss or bushing 2I9 carried by the bottom wall of each blade 2I9 and 2I9. The pin 2" is adapted to engage in the inner wall or head" 2I9 similar to the structure shown in Figure 11. The cylindrical side wall 299 is provided with an upper opening 2 I9 disposed at one side of a fixed blade and is also provided-with a lower opening 229 disposed on the opposite side of the same blade. The side wall 299 is also provided with a pair oi intermediate openings HI and 222, which are adapted to be disposed on opposite sides of the other of the stationary blades.

The opening 2I9 is disposed in position-for registry with the upper pair or passages I94 and I99 upon rotation oi the rotor 299, and the lower opening 229 is disposed in a position for registry with the lower pair oi openings 299 and 2M.

The intermediate opening 22I is disposed in a- 224 are disposed within the cylinder 299 be-' 7 tween the blades 2I5 and 2I6, and the blades 229 and 229 are fixedly secured to a drive shaft 229 by means 01 a holding member 229, which engages through bosses 221 and 229 carried by the blades 222 and 229 respectively. The blades 229- and 229 are similar 'in every detail to the blades 99 and .99. -being of sector configuration and the flat opposite faces cbniront or substantially contact with i the opposite flat faces of the blades 2I5 and 12I9 The shaft 229 is provided with a reduced elongated extension 229, which extends downwardly into the gear hou I99. A gear 299 is keyed onto the shaft 229 in the gear housing I99, the gear 299 being eccentric to the shaft 229. A pair oi balance weights 22I and 222 are also keyed onto the shaft 229 on opposite sides of the gear 299 and are onset opposite from the gear 299, as shown in Figure 13. The gear 229 is in constant mesh with a gear 292, which is keyed to a jack shaft 229. The Jack shaft 234 is rotatably mounted at its upper end in an anti-friction bearing structure 299, which is mounted in an annular plate or head 229, which is seated on a shoulder 291 at the inner end of the cylinder I99. The plate or head 236 provides a partition between the cylinder I95 and the gear housing I 99 and also provides a means for rotatably' supporting the upper or outer ends of the pair of jack shafts.

A cylindrical sleeve 299 is mounted about the jack shaft 239 and at its upper end bears against the anti-friction bearing 225. Preferably the sleeve 239 is tight on the shaft 239 so that the shaft 299 is thereby held against endwise movement in one direction by contact of th sleeve 29% with the anti-friction bearing 235.

The jack shaft 239 has keyed thereon a pair of balancing weights, 239 and 259, which are disposed on opposite sides oi the gear 233 and are arranged eccentrically with respect to the shaft 284 opposite from the eccentricity of the ear 233. The jack shaft 234 also has keyed thereon a second gear 2, which is eccentric to the shaft 234 in a position opposite from the eccentricity of the gear 233. A pair of balancing weights 242 and 243 are keyed to the lack shaft 234 on opposite sides of the gear 24f and are eccentric to the shaft 234 in opposed relation to the eccen tricity of the gear 24I.

The lower end of the jack shaft 234 is rotatably mounted in an anti-friction bearing 244, which is mounted in a lower plate or head 285 seating on a shoulder or seat 248. Preferably the lower end of the shaft 234 is provided with a reduced threaded portion 241 on which a holding nut 248 is threaded. The gear 2 is adapted to mesh with a centrally disposed eccentric driving gear 249, which is eccentrically carried by an auxiliary driving shaft 258. The peripheral surface of the shaft 258 is formed with flat faces. which are engaged by the eccentric driving gear '248.

A pair of balancing weights 25I and 252 are mounted on the shaft member 258 on opposite sides of the eccentric driving gear 249. The lower end portion of the shaft 229 is provided with a reduced stub shaft 253, which rotatably engages in a bushing or sleeve 254 carried by the shaft member 258. The shaft member 258 engages in a hollow shaft 255, which is rotatable in a bearing sleeve 258. The sleeve 288 is snugly mounted in the lower or outer wall or head 251 of the bearing housing I88. The sleeve 255 is provided with a nut socket 258 within which the shaft 258 engages so that the shaft 258 will rotate with the sleeve 255. Preferably a cylindricai packing 259 is mounted on a reduced stub 288 carried by the shaft 258, so as to provide a cushioning means for the lower end of the shaft 258.

A square shaft 28I engages in a nut ocket 282 formed in the outer end of the sleeve 55 and a splined coupling member 283 is formed integral with the square shaft 28I and is adapted to be connected to a suitable operating means. The shaft 28I is preferably formed so that it will tightly fit into the nut socket 282 in order that the shaft 28I will be held against endwise movement with respect to the sleeve shaft 255.

An eccentrically disposed gear member 283 is disposed in the gear housing I88 and meshed with the eccentric driving gear 249 diametrically opposite from the gear 2. The gear 283 is keyed to a second jack shaft 284 and a pair of balancing weights 285 and 288 are also keyed to the jack shaft 284 on opposite sides of the gear 283. The lower end of the jack shaft 284 is rotatably mounted in an anti-friction bearing 281, which is seated in a recess 288 formed in the inner plate or head 245. The jack shaft 284 is provided at its lower end with a reduced threaded member 289 on which a holding nut 218 is threaded.

The upper end of the lack shaft 284 is rotatably mounted in an upper anti-friction bearing 2" carried by the partition or head 238. An eccentric gear 212 iskeyed to the jack shaft 284 above the gear 283 and a pair of balancing weights 218 and 214 are disposed on opposite sides of the gear 212 and are also keyed to the jack shaft 284.

A rotor driving gear 215 meshes with the cocentric gear 212 and is snugly mounted on a square end 218 of a sleeve shaft 211. The sleeve shaft 211 is provided with an outer flat nut conconstruction which is adapted to engage within the nut socket 2. A cylindrical bushing 218 is disposed between the inner cylindrical surface of the sleeve 211 and the peripheral surface of the reduced shaft 228. A bearing sleeve 219 is mounted in the plate 238 and the hollow shaft H3 is rotatable within the sleeve or bearing 219. The bearing 219 is provided with a flange 288, which not only holds the sleeve 219 against inward endwise movement, but also acts as a spacing means and a bearing forthe rotor 288.

The housing I84 is provided with an upper head or plate 28I havin an annular flange or rib 282 engaging in an annular groove 283 formed in the cylinder I85. The head 28I is detachably secured to the cylinder I85 by fastening devices 284. The head 28I is formed centrally thereof with an upwardly offset boss or bushing 285, within which an anti-friction bearing 288 is mounted. The rotor head 2 is provided centrally thereof with a stub shaft 281 which engages the anti-friction bearing 288 so that the rotor 288 will be held concentrically of the cylinder I85. The boss or bushing 285 is provided with a threaded opening 288, which may serve as a means for receiving a threaded supporting member or, if desired may serve as a means for connecting the housing I84 with a source of lubricant supply, which maybe discharged into the bushing 285 and be forced through the antifriction bearing 288 and then downwardly into the gear housing I88. The gear housing I88 is preferably filled with a suitable lubricant, so that the eccentric gears will be lubricated at all times.

In operation, the blades 85 and 88 will rotate at a constant speed whereas the rotor 88 with the blades 81 and 88 will rotate at variable speeds during each complete revolution thereof. These variable speeds are accomplished by the eccentric gearing which in one cycle causes the advance of the blades 81 and 88 until one face of each of such blades substantially contacts with a face of each blade 85 and 88 to thereby exhaust the fluid therebetween. In another cycle the blades 81 and 88 with the rotor 88 are retarded in their rotation, so..that the blades 85 and 88 rotate at a greater speed than the blades 81 and 88, and the opposite faces of blades 81 and 88 substantially contact with the opposite faces of blades 85 and 88.

The eccentric gearing also provides an interval between each of the aforesaid cycles when all of the blades rotate as a unit and at the same speed. At these intervals the contacting blades are passing the walls between the inlet and outlet passages of .one or more pairs of circumferentially aligned passages.

With the construction shown in Figures 13 to 17, the operation of the blades is similar to the structure shown in Figures 1 to 12, with the exception that the both pairs of blades 2I5, 2I8 and 223 and 224 are rotated at'variable speeds, the blades -2I5, 2I8 being accelerated while the blades 223, 224 are simultaneously retarded in their rotation during one cycle and in another cycle the blades 223, 224 are accelerated while the blades 2I5, 2I8 are simultaneously retarded.

thus providing the effect of an oscillation of both pairs of blades. Furthermore, by providing eccentric driving gears for both pairs of blades they are given accelerated movement toward and from each other.

With respect to long fluid passages in the liner 38, it might be stated that these are provided) in order to provide for the intake and exhaust of the fluid on that cycle, designated the retarded cycle, wherein the short radius of the driving gear is effecting movement of the rotor, the driving gear at this time retarding the rotation of one pair of blades, as for example retarding the rotation of blades 61 and 68 until the cycle is completed. During this cycle the rotor 60 travels circumferentially a greater distance and thus. making it necessary to elongate an inlet and an outlet passage, whereas on the other or accelerated cycle the inlet and outlet passages are much shorter due to the fact that the long radius of the eccentric driving gear is operating on the short radius of the driven eccentric. During the time that the driving gear is working in the accelerated cycle, the exhaust and intake occurs in a shorter circumferential space than for the retarded cycle. The circumferential offsetting of the pairs of superposed passages compensates for the interval between the operating cycles when both pairs of blades are rotating as a unit and prevents leakage of the fluid following the suction stroke.

The overlapping of a short intake passage with a long intake passage, as for example, short passage 38 with long passage ll provides for an increased port area during the accelerated cycle so that the fluid may be more readily drawn into the cylinder in an equal quantity on the accelerated cycle as on the decelerated cycle. The overlapping of the short and long outlet passages permits the exhausting of the fluid on the accelerated cycle without excessive pressure being exerted on the operating parts.

What I claim is:

l. A fluid pump comprising a housing including a cylinder and a gear chamber, said housing having an inlet and outlet port communicating with said cylinder, a cylindrical liner in said cylinder provided with pairs of elongated fluid passages, said pairs of passages being spaced longitudinally of said liner, one passage of each pair of passages communicating with said inlet port, and the other passage of each pair communicating with said outlet port, a cylindrical piston rotatable in said liner and having a plurality oi openings spaced apart circumferentially of said piston, said openings being registerable with said passages, a pair of opposed blades 'fixed within said piston between said openings, a pair of rotary blades between said fixed blades and movable relative to said piston and said fixed blades for alternately efl'ecting suction within and exhaustion of the fluid from said piston, and

gear means in said gear chamber operatively connected with said piston and said rotary blades for rotating said piston at varying speeds while simultaneously rotatating said rotary blades.

2. In a pump having inlet and outlet ports, pairs of relatively movable rotary pumping elements correlated with said ports and having communication therewith, means operatively connected with said elements for effecting operation thereof to thereby provide an accelerated pumping cycle for said elements and a retarded pumping cycle for said elements during each revolution of said elements, and a ported stationary cylindrical member about said elements. said member having series of elongated fluid passages the passages of each series being spacedlongi tudinally of said liner with respect to the passages of each other series, one passage of each series being substantially longer than the other passage of the same series to thereby provide communication between said ports and said elements during the retarded cycle, and the shorter passage of each series providing communication between said ports and said elements during the accelerated cycle.

3. In a pump having inlet and outlet ports, pairs of relatively movable rotary pumping elements correlated with said ports, eccentric gear means for effecting operation of said elements to thereby provide alternate accelerated and retarded pumping cycles for said elements during each revolution of said elements, and liner means about said elements for providing communication of said elements with said ports during each cycle thereof, said latter means including a cylindrical member formed with pairs of parallel passages, said pairs of passages being spaced longitudinally of said liner means, and one passage of each pair being longer than the other passage of each pair to thereby provide communication between said ports and said elements during the retarded cycle thereof, the remaining or short passage of each pair providing communication between said ports and said elements during the accelerated cycle thereof.

4. In a pump having inlet and outlet ports, pairs of relatively movable rotary pumping elements correlated with said ports, eccentric gear means for effecting operation of said elements to thereby provide alternate accelerated and retarded pumping cycles for said elements during each revolution. of said elements, and liner means about said elements for providing communication of said elements with said ports during each cycle thereof, said latter means including a cylindrical member formed with pairs of parallel passages, said pairs of passages being spaced longitudinally of said liner means, and one passage of each pair being longer than the otherpassage of each pair to thereby provide communication between said ports and said elements during the retarded cycle thereof, the remaining or short passage of each pair providing communication between said ports and said elements during the accelerated cycle thereof, said member also having means outwardly of said elements for communicating the long passage of one pair with the short passage of an adjacent pair.

5. In a pump, relatively movable rotary pumping elements. and operating means therefor. said operating means including a drive shaft, an eccentrically disposed circular'driving gear flxed to said shaft, a pair of jack shafts. a circular eccentrically disposed gear iixed to each jack shaft and meshing with said drivin Gear, 9. second circular eccentrically disposed gear fixed to each jack shaft and positioned with the long radius thereot opposite to the long radius oi. the first jack shaft gear, an eccentric gear operatively connected with certain of said elements and with one of said second lack shalt gears, and an eccentric gear operatively connected with the remaining of said elements and with the other of said second lack shalt gears.

6. A fluid pump comprising a housing having inlet and outlet ports, a cylindrical liner fixed in sald housing, said liner being provided with longitudinally spaced apart pairs of elongated open having peripheral passages communicating the long opening of one pair with the short opening oi an adiacent pair oi openings. one opening or each pair constituting an outlet passage and the other opening of each pair constituting an inlet passage, a cylindrical body rotatable within said liner and formed with an opening for each pair 01' liner openings, a pair of pumping blades fixed in said body, a second pair of pumping blades movable in said body between said fixed blades, means rotating said body, and means for moving said movable blades relative to said fixed blades.

'7. In a pump having inlet and outlet ports, a cylindrical stationary member, pumping means movable in said member, said member having longitudinally spaced apart pairs of elongated openings disposed in parallel relation, one opening of each pair being long and the other opening 01' each pair being short. alternate ones or said long openings being outlet openings, the remaining ones of said long openings being inlet openings, alternate ones 01' said short openings being outlet openings, the remaining ones oi said short openings being inlet openings, means communicating said outlet openings with each other and with said outlet port, means communicating said inlet openings with each other and with said inlet port, and operating means for said pumping means.

8. In a pump having inlet and outlet ports, a cylindrical stationary member, pumping means movable in said member, said member having longitudinally spaced apart pairs of elongated openings disposed in parallel relation, one opening of each pair being long and the other opening of each pair being short, alternate ones of said long openings being outlet openings, the remaining ones of said long openings being inlet openings, alternate ones or said short openings being outlet openings, the remaining ones of said short openings being inlet openings, means. commalnins ones oi said long openings being inlet openings, alternate ones or said short openings being outlet openings. the remaining ones or said short openings being inlet openings, means communicating said outlet openings with each other and with said outlet port, means communicating said inlet openings with each other and with said inlet port, and means operating said pumping means to provide accelerated pumping cycles when said pumping means is in confronting position to said short openings and to provide retarded pumping cycles when said pumping means is in confronting position to said long openings.

10. In a pump having inlet and outlet ports, a cylindrical stationary member, pumping means movable in said member, said member having longitudinally spaced apart pairs of elongated openings disposed in parallel relation, one open- -ing oi. each pair being long and the other opening oi each pair being short, alternate ones of said long openings being outlet openings, the remaining ones of said long openings being inlet openings, alternate ones oi said short openings being outlet openings, the remaining ones of said short openings being inlet openings, a short outlet opening overlapping an adiacent long outlet opening, a short inlet opening overlapping an adjacent long inlet opening, means communicating said outlet openings with each other and with said outlet port, means communicating said inlet openings with each other and with said in let port, and operating means for said pumping means.

11. A fluid pump comprising a. housing having inlet and outlet ports, aliner fixed in said housing having pairs of longitudinally spaced apart pasmunicating said outlet openings with each'other and with said outlet port, means communicating said inlet openings with eachother and with said inlet port, and means operating said pumping means to thereby provide alternate accelerated and retarded pumping cycles.

9. In a pump having inlet and outlet ports, a cylindrical stationary member, pumping means movable in said member, said member having longitudinally spaced apart pairs of elongated openings disposed in parallel relation, one opening of each pair being long and the other opening 01' each pair being short, alternate ones of said long openings'being outlet openings, the resages, one passage of each pair of passages being an outlet passage and the other passage of each pair being an' inlet passage, said liner having means communicating the outlet passages with each other and with said outlet port and also having means communicating the inlet passages with each other and with said inlet port, a closed rotor in said liner having openings coplanar with each pair of passages, a pair of pumping blades fixed in said rotor, a second pair of pumping blades in said rotor and movable relative to said fixed blades, means rotating said second pair of blades at a constant speed, and means rotating said rotor at alternate. accelerated and retarded cycles to thereby efi'ect movement of said pairs 01' blades relative to each other, said passages being so arranged circumferentially about said rotor as to register with the openings of said rotor during each cycle of the latter.

GEORGE T. DOWNEY. 

